JP7371869B2 - Transmission device, electric vehicle including the device, and method for driving the device - Google Patents

Description

TECHNICAL FIELD The present disclosure relates to a transmission device, and more particularly to a transmission device having dual power sources.

When a transmission with planetary gears is operated, the key problem is that the gap between the tooth surfaces (also known as backlash) that occurs when the teeth mesh cannot be eliminated, so the direction of movement of the gears changes frequently. Sometimes, due to phenomena such as vibration, noise, and wear caused by the impact between the teeth due to backlash, the service life of the transmission is shortened and problems such as inaccurate operation accuracy occur. Some high precision, miniaturization, large torque, advanced products where the output direction is frequently changed, such as RV reducer at each motion joint location in industrial robot structure, the high positioning accuracy of RV reducer and very In order to reach a long service life, the requirements for material selection and manufacturing accuracy of RV reducers are very high, thus inevitably leading to an increase in manufacturing costs. However, no matter how high the machining accuracy is, it is not possible to completely eliminate the gaps between the tooth surfaces when the teeth mesh (see Fig. 3). For example, when the direction of movement of a planetary gear changes frequently, it is frequently subjected to the impact of two forces in different directions on the tooth surface of a fixed internal toothed ring, no matter how small the gap between the gears. The flank gaps between teeth are also frequently transformed. As the gears wear out, the flank gaps between the teeth accelerate and widen, rendering the RV speed reducer ineffective.

In addition, as is well known, FM motors are currently widely used in electric vehicles. FM motors have high efficiency during high-speed driving, about 94%, but low efficiency during low-speed driving, below about 70%. Yes (see Figure 4). However, during the driving process of an electric vehicle, it is necessary to frequently accelerate or decelerate according to changes in road conditions, and in the process from low-speed driving to high-speed driving, a lot of electrical energy is wasted. In an electric car, energy is turned into heat and passed through the cooling water.

Furthermore, the frequency conversion motor of an electric vehicle may become overloaded when starting the vehicle or climbing a hill with a load applied, and the peak value of the motor output may reach more than twice the rated output. The above two issues are the keys to the ability of electric vehicles to reach their designed mileage.

The present disclosure is made to solve the deficiencies in the prior art, and provides a transmission device with dual power sources, comprising a planetary gear assembly driven by the dual power sources, the planetary gear assembly comprising: the dual power source includes an input shaft connected to the sun gear, the dual power source includes an input shaft connected to the sun gear; a shaft drives the sun gear to rotate in a first direction relative to its own axis of rotation; the dual power source is connected to the rotating internal gear ring; driven to rotate in a second direction opposite to the first direction relative to an axis of rotation of the planetary gear, wherein the planetary gear rotates in the second direction relative to its own axis of rotation (e.g. The rotating internal tooth ring and the planetary gear are rotated by the drive of the dual power source by a synchronizer (ensuring that the rotation direction of the rotating internal tooth ring and the planetary gear are the same), and the rotational movement direction of the planetary gear around the input shaft is the same as that of the rotating internal tooth ring. A transmission device is provided in which the linear velocity V1 of the pitch motion of a ring and the linear velocity V2 of the pitch motion of the sun gear are determined.

According to one aspect of the present disclosure, the dual power sources include a first power source arranged to drive the sun gear by the input shaft and a first power source arranged to drive the rotating internal gear ring. and a second power source.

According to each of the above aspects of the present disclosure, the planetary gear is attached to a planetary gear cage in which an output shaft is installed, the sun gear is installed coaxially with the rotating internal gear ring, and the output shaft is connected to the input shaft. coaxially installed.

According to each of the above aspects of the present disclosure, when the first direction is a clockwise direction, when the second direction is a counterclockwise direction, and when the first direction is a counterclockwise direction, The second direction is a clockwise direction.

According to each of the above aspects of the present disclosure, when V1>V2, the rotational direction of the planetary gear and the planetary gear cage around the input shaft is opposite to the rotational direction of the input shaft, and The direction of rotation of the planet gear is opposite to the direction of rotation of the input shaft, and the gap between the tooth surfaces of the planetary gear and the tooth surface of the rotary internal tooth ring that meshes with the planetary gear is on one side of the teeth of the planetary gear. Located only in

When V1<V2, the rotation direction of the planetary gear and the planetary gear cage around the input shaft is the same as the rotation direction of the input shaft, and the rotation direction of the output shaft itself is the same as the rotation direction of the input shaft. The gap between the tooth surface of the planetary gear and the tooth surface of the rotary internal tooth ring that meshes therewith is maintained on the one side of the tooth of the planetary gear.

When V1=V2, the rotational speed of the planetary gear and the planetary gear cage around the input shaft is zero, and the rotational speed of the output shaft itself is zero.

According to each of the above aspects of the present disclosure, a parallel gear is installed on the rotary internal tooth ring, and the internal ring drive gear driven by the second power source meshes with the parallel gear, so that the rotary internal tooth The ring is driven.

According to each of the above aspects of the present disclosure, a sun gear front gear is installed on the input shaft, and a sun gear drive gear driven by the first power source meshes with the sun gear front gear, so that the sun gear is driven.

According to each of the above aspects of the present disclosure, the first power source has a constant power output, the second power source has a speed adjustable power output, and the electronic control device is connected to the first power source by an input control line. the first power source is connected to a power source, and handles the error of rotation speed drop or instability when the first power source has different power.

According to each of the above aspects of the present disclosure, when the second power source rolls with the rotating internal toothed ring, the real-time data collection line connected to the second power source causes the rotational internal toothed ring to rotate. Motion data is transmitted to the electronic control device, and the electronic control device controls and adjusts the power output of the second power source power source through the real-time data acquisition line by processing an internal program or an external command, and controls and adjusts the power output of the second power source power source through the real-time data acquisition line. Able to reach different speeds required by the working situation.

According to each of the above aspects of the present disclosure, the first power source is a speed-adjustable power output, and the electronic control device controls the power output of the first power source through an input control line.

According to the above aspects of the present disclosure, the first power source and the second power source are controllable and speed adjustable power machines.

According to the above aspects of the present disclosure, the controllable, speed adjustable power machine is an electric motor or an internal combustion engine.

According to the present disclosure, there is further provided an electric vehicle including the transmission device having the dual power source according to each of the above aspects.

The present disclosure provides a driving method for driving the transmission device described above, wherein the transmission device includes a dual power source driving a planetary gear assembly, the planetary gear assembly including a sun gear and a rotating internal gear. a planetary gear meshing between the sun gear and the rotating internal gear ring, the dual power source includes an input shaft connected to the sun gear, and the input shaft drives the sun gear. the dual power source is arranged to drive the rotating internal toothed ring to rotate in a first direction relative to its own axis of rotation; driven to rotate in a second direction opposite to the first direction, wherein the planetary gear rotates in the second direction relative to its own axis of rotation, and the planetary gear rotates in the second direction relative to its own axis of rotation; The driving method is further provided, wherein the rotational movement direction around the input shaft is determined by a linear velocity V1 of the pitch motion of the rotary internal gear ring and a linear velocity V2 of the pitch motion of the sun gear.

According to one aspect of the driving method described above, the dual power source includes a first power source and a second power source, and the first power source is arranged to drive the sun gear by the input shaft. and the second power source is arranged to drive the rotating internal tooth ring.

According to each aspect of the driving method described above, the planetary gear is attached to a planetary gear cage, the output shaft is installed in the planetary gear cage, the sun gear is installed coaxially with the rotating internal gear ring, and the output shaft is installed coaxially with the input shaft.

According to each aspect of the driving method described above, when the first direction is a clockwise direction, the second direction is a counterclockwise direction, and the first direction is a counterclockwise direction, , the second direction is a clockwise direction.

According to each aspect of the driving method described above, when V1>V2, the rotational direction of the planetary gear and the planetary gear cage around the input shaft is opposite to the rotational direction of the input shaft, and the output The direction of rotation of the shaft itself is opposite to the direction of rotation of the input shaft, and the gap between the tooth surface of the planetary gear and the tooth surface of the rotary internal tooth ring that meshes with it is one of the teeth of the planetary gear. Located only on the side.

When V1<V2, the rotation direction of the planetary gear and the planetary gear cage around the input shaft is the same as the rotation direction of the input shaft, and the rotation direction of the output shaft itself is the same as the rotation direction of the input shaft. The gap between the tooth surface of the planetary gear and the tooth surface of the rotary internal tooth ring that meshes therewith is maintained on the one side of the tooth of the planetary gear.

When V1=V2, the rotational speed of the planetary gear and the planetary gear cage around the input shaft is zero, and the rotational speed of the output shaft itself is zero.

According to each aspect of the driving method described above, the first power source is installed as a constant power output, the second power source is installed as a speed adjustable power output, and the input control line is connected to the An electronic control device is installed to handle errors of rotational speed drop or instability when the first power source has different power.

According to each aspect of the driving method described above, the second power source rolls with the rotating internal toothed ring, and the real-time data collection line connected to the second power source causes the rotating internal toothed ring to rotate. Motion data is transmitted to the electronic control device, and the electronic control device controls and adjusts the power output of the second power source power source through the real-time data acquisition line by processing an internal program or an external command, and controls and adjusts the power output of the second power source power source through the real-time data acquisition line. Able to reach different speeds required by the working situation.

According to each aspect of the driving method described above, the first power source is installed as a speed-adjustable power output, and the electronic control device controls the power output of the first power source by an input control line. .

According to each aspect of the driving method described above, the first power source and the second power source are installed like controllable and speed adjustable power machines.

According to aspects of the drive method described above, the controllable, adjustable speed power machine is an electric motor or an internal combustion engine.

According to each aspect of the driving method described above, a parallel gear is installed in the rotating inner toothed ring, and the inner toothed ring driving gear driven by the second power source meshes with the parallel gear, so that the rotating inner ring is engaged with the parallel gear. The tooth ring is driven.

According to each aspect of the driving method described above, a sun gear front gear is installed on the input shaft, and a sun gear drive gear driven by the first power source meshes with the sun gear front gear, so that the sun gear Gears are driven.

One of the features of the transmission device with dual power sources according to the present disclosure is that it applies a mechatronic composite structure, and generates teeth when the teeth of the planetary gear and the teeth of the internal tooth ring mesh during operation of the planetary gear transmission. The key problem of not being able to remove gaps between surfaces (also called backlash) is solved from the beginning. In particular, gears solve defects such as vibration, noise, wear and tear caused by backlash and impact between teeth when the direction of movement is frequently changed, extending the service life of the transmission and improving operating accuracy. Guarantee.

The transmission device with dual power sources according to the present disclosure is suitable for high precision, small size, large torque, and advanced products where the output direction is frequently changed, such as in industries where RV reducers are installed at each motion joint. It may also be applied to robot structures. The present disclosure provides high positioning accuracy and a very long service life for RV reducers. In particular, when the movement direction of the planetary gear is frequently changed, the tooth surface of the rotating internal tooth ring is not often subjected to the impact of two forces in different directions, and the backlash between the teeth is also frequently changed. never be done. Furthermore, even if the gears are worn out, the speed adjustment control of the electronic control device prevents the backlash between the teeth from accelerating and increasing, thereby avoiding ineffectiveness of the RV speed reducer.

In the dual power transmission device of the present disclosure, the output shaft can conveniently rotate forward or backward when the sun gear, the planetary gear, and the rotary internal gear ring remain unchanged in their rotation direction (Fig. 2 ), but the backlash between the teeth remains only on one side, and the direction in which the force is received between the teeth does not change, so the direction of the output shaft changes frequently, causing The backlash between the teeth is not changed. Since the teeth mesh tightly on only one side during operation, no impact force is generated due to backlash conversion. Therefore, the positioning accuracy of the transmission device according to the present disclosure is higher, and the service life thereof is longer. In addition, even if there is large wear between the teeth and the backlash between the teeth increases, the other surfaces of the teeth are tightly meshed, so the correction control of the electronic control device ensures perfect The positioning accuracy and usage effect can be reached.

The transmission device with dual power sources according to the present disclosure is also applied to the transmission of a battery electric vehicle, the two electric motors of which can operate completely within the maximum efficiency speed range of the frequency conversion motor during frequency conversion. Additionally, the output shaft may have zero rotational speed or continuously variable speed in forward and reverse directions. It can also generate the required torque, which is several tens of times more powerful than conventional battery electric vehicles. If the conventional EVB320-140-180 frequency conversion motor is adopted, its rated power is 30KW, the peak power is 60KW, but the peak torque is only 180N·M. When a battery electric vehicle drives, its speed changes frequently depending on the road conditions, and the battery electric vehicle has to repeatedly accelerate from static to dynamic, climb different slopes, and carry different loads, so conventional The frequency converting motors employed by battery electric vehicles require large reserve power and low efficiency regions where the motors operate at less than 70% for long periods of time.

However, under the same road condition driving condition, according to the present disclosure, two dual power transmission devices of 10KW each may be adopted, the total power is only 20KW, and the maximum torque is 9000N・M to 10,000 N·M (as shown in FIG. 5), and the two motors continue to operate in the high efficiency region of 95%. The large torque, which is more than 9000 N·M, can fully satisfy the driving of battery electric vehicles in all road conditions.

Comparing a conventional frequency conversion motor with a peak power of 60KW and a peak torque of 180N・M to the dual power transmission device of the present disclosure with a power of 20KW and a maximum torque of 9000N・M or more, it is equivalent. For a battery electric vehicle based on operating road conditions, if the transmission device of the present disclosure is adopted, the motor can continue to operate within the high efficiency operating speed range and avoid the low efficiency region of low speed operation due to frequency conversion. Therefore, the conclusion can be drawn that when driving under comparable road conditions, a motor with lower power may be selected and placed. Therefore, if the dual power planetary gear transmission device of the present disclosure is adopted for the conventional battery electric vehicle, it can greatly adapt to the driving conditions of the vehicle and greatly extend its mileage. Dual power sources in the present disclosure may select a controllable, adjustable speed high power internal combustion engine or other power machine when a high power and high torque output transmission device is required. The content of the present disclosure may be applied to other mechanical products that require forward/reverse rotational speed change.

FIG. 1 is a schematic diagram showing a transmission device having dual power sources according to the present disclosure. FIG. 2 illustrates the backlash between the rotating internal ring teeth and the planet gear teeth when the sun gear according to the present disclosure is rotated in a clockwise direction. FIG. 3 shows that backlash exists in a transmission device with a conventional planetary gear assembly in the prior art. FIG. 4 shows a torque diagram of a conventional FM motor. FIG. 5 shows a torque diagram of a transmission device with dual power sources according to the present disclosure.

Hereinafter, embodiments of the present disclosure will be described in detail with reference to the drawings.

FIG. 1 shows a schematic diagram of a transmission device with dual power sources according to the present disclosure, and according to one embodiment of the present disclosure, the transmission device with dual power sources is driven by the dual power sources. Includes planetary gear assembly.

The planetary gear assembly includes a sun gear 3, a rotating internal toothed ring 4, and a planetary gear 5 meshing between the sun gear 3 and the rotating internal toothed ring 4.

The dual power source includes an input shaft 14 connected to the sun gear 3, a first power source 1, and a second power source 2, the input shaft 14 directs the sun gear 3 to its own rotation axis. said dual power source is connected to said rotating internal toothed ring 4 and configured to drive said rotating internal toothed ring 4 relative to its own axis of rotation. and is driven to rotate in a second direction opposite to the first direction, wherein the planetary gear 5 rotates in the second direction relative to its own axis of rotation, and the planetary gear 5 rotates in the second direction with respect to its own axis of rotation. The direction of rotation around the input shaft 14 is determined by the linear velocity V1 of the pitch motion of the rotary internal gear ring 4 and the linear velocity V2 of the pitch motion of the sun gear 3.

According to one embodiment of the present disclosure, the first power source 1 is arranged to drive the sun gear 3 by the input shaft 14, and the second power source 2 is arranged to drive the sun gear 3 by means of the input shaft 14. It is arranged to drive the ring 4.

According to the above-mentioned embodiments of the present disclosure, the planetary gear 5 is attached to a planetary gear cage 6 on which an output shaft 7 is installed, the sun gear 3 is coaxially installed on the rotating internal gear ring 4, and the The output shaft 7 is installed coaxially with the input shaft 14 .

According to each of the above embodiments of the present disclosure, when the first direction is a clockwise direction, the second direction is a counterclockwise direction, and the first direction is a counterclockwise direction, , the second direction is a clockwise direction.

According to each of the above embodiments of the present disclosure, when V1>V2, the rotational direction of the planetary gear 5 and the planetary gear cage 6 around the input shaft 14 is opposite to the rotational direction of the input shaft 14. Therefore, the rotational direction of the output shaft 7 itself is opposite to the rotational direction of the input shaft 14, and the tooth surface between the tooth surface of the planetary gear 5 and the tooth surface 16 of the rotary internal gear ring 4 that meshes therewith. The gap (also called backlash) is located only on one side of the teeth of the planetary gear 5. For example, as shown in FIG. 2, when the input shaft 14 drives the sun gear 3 to rotate in a clockwise direction relative to its own axis of rotation, the output shaft 7 itself rotates in a counterclockwise direction. During rotation, the gap between the tooth surfaces is located only on the right side of the teeth of the planetary gear 5, but the left side of the teeth of the planetary gear 5 is in contact with the tooth surface of the rotating internal gear ring 4. When the input shaft 14 drives the sun gear 3 to rotate in a counterclockwise direction relative to its own axis of rotation (not shown), the output shaft 7 itself rotates in a clockwise direction and the Those skilled in the art will understand that the tooth flank gap is located only on the left side of the teeth of the planetary gear 5, but the right side of the teeth of the planetary gear 5 is in contact with the tooth flank of the rotary internal gear ring 4.

When V1<V2, the rotation direction of the planetary gear 5 and the planetary gear cage 6 around the input shaft 14 is the same as the rotation direction of the input shaft 14, and the rotation direction of the output shaft 7 itself is the same as the rotation direction of the output shaft 7 itself. The direction of rotation is the same as the rotation direction of the input shaft 14, and the gap between the tooth surfaces of the planetary gear 5 and the tooth surface of the rotary internal tooth ring 4 that meshes therewith is on the one side of the teeth of the planetary gear 5. Retained. For example, as shown in FIG. 2, when the input shaft 14 drives the sun gear 3 to rotate in a clockwise direction relative to its own axis of rotation, the output shaft 7 itself rotates in a clockwise direction. However, the gap between the tooth surfaces is still located only on the right side of the teeth of the planetary gear 5, and the left side of the teeth of the planetary gear 5 is still in contact with the tooth surface of the rotating internal gear ring 4. When the input shaft 14 drives the sun gear 3 to rotate in a counterclockwise direction relative to its own axis of rotation (not shown), the output shaft 7 itself rotates in a counterclockwise direction; It will be understood by those skilled in the art that the tooth flank gap is still located only on the left side of the teeth of the planetary gear 5, but the right side of the teeth of the planetary gear 5 is still in contact with the tooth flank of the rotating internal gear ring 4. It can be understood.

When V1=V2, the rotational speed of the planetary gear 5 and the planetary gear cage 6 around the input shaft 14 is zero, and the rotational speed of the output shaft 7 itself is zero.

According to each of the above aspects of the present disclosure, the parallel gear 8 is installed on the rotary internal ring 4, and the internal ring drive gear 9 driven by the second power source 2 meshes with the parallel gear 8. , the rotary internal gear ring 4 is driven.

According to each of the embodiments of the present disclosure, the sun gear front gear 10 is installed on the input shaft 14, and the sun gear drive gear 15 driven by the first power source 1 meshes with the sun gear front gear 10. Accordingly, the sun gear 3 is driven.

By installing the internal ring drive gear 9 and the parallel gear 8 to mesh with each other, and by installing the sun gear drive gear 15 and the sun gear front gear 10 to mesh with each other, a particularly large volume and high power power source is required. At times, more space can be provided for accommodating the first and second power sources.

According to the above embodiments of the present disclosure, the first power source 1 has a constant power output, the second power source 2 has a speed adjustable power output, and the electronic control device 11 has an input control line 13. In this way, the error of rotational speed drop or instability when the first power source 1 has different electric power is handled.

According to each of the above embodiments of the present disclosure, when the second power source 2 rolls with the rotating internal tooth ring 4, the real-time data acquisition line 12 connected to the second power source 2 The motion data of the rotary internal gear ring 4 is transmitted to the electronic control device 11, and the electronic control device 11 controls the power output of the second power source 2 through the real-time data acquisition line 12 by processing an internal program or an external command. can be controlled and adjusted to reach various speeds of the output shaft 7 as required by the working situation.

According to each of the above embodiments of the present disclosure, the first power source 1 has a speed adjustable power output, and the electronic control device 11 controls the power output of the first power source 1 through the input control line 13. do.

Due to the correction control of the electronic control device 11, the tooth flank gap between the tooth flank of the planetary gear 5 and the tooth flank of the rotary internal tooth ring 4 that meshes therewith is located only on one side of the teeth of the planetary gear 5. It helps to keep it like that.

According to the above embodiments of the present disclosure, the first power source and the second power source are controllable and speed adjustable power machines.

According to the above embodiments of the present disclosure, the controllable, adjustable speed power machine is an electric motor or an internal combustion engine.

In the dual power transmission device of the present disclosure, when the sun gear 3, the planetary gear 5, and the rotary internal gear ring 4 remain in their own rotational directions, the output shaft 7 can conveniently rotate in the forward or reverse direction. However, the backlash between the teeth remains on only one side, and the direction in which the force between the teeth is received does not change, so the direction of the output shaft 7 changes frequently. This does not change the backlash between the teeth. Since the teeth mesh tightly on only one side during operation, no impact force is generated due to backlash conversion. Therefore, the positioning accuracy of the transmission device according to the present disclosure is higher, and the service life thereof is longer. In addition, even if there is large wear between the teeth and the backlash between the teeth increases, the other surfaces of the teeth are tightly meshed, so the correction control of the electronic control unit 11 ensures a perfect fit. Good positioning accuracy and usage effect can be reached.

According to the content of the present disclosure, there is further provided an electric vehicle including the transmission device having the dual power sources described in each of the embodiments.

The transmission device with dual power sources according to the present disclosure is applied to the transmission of a battery electric vehicle, the two electric motors of which can operate completely within the maximum efficiency speed range of the frequency conversion motor during frequency conversion. Additionally, the output shaft 7 may have zero rotational speed or continuously variable speed in forward and reverse directions. It can also generate the required torque, which is several tens of times more powerful than conventional battery electric vehicles.

If the conventional EVB320-140-180 frequency conversion motor is adopted, its rated power is 30KW, the peak power is 60KW, but the peak torque is only 180N·M. When a battery electric vehicle drives, its speed changes frequently depending on the road conditions, and the battery electric vehicle has to repeatedly accelerate from static to dynamic, climb different slopes, and carry different loads, so conventional The frequency converting motors employed by battery electric vehicles require large reserve power and low efficiency regions where the motors operate at less than 70% for long periods of time.

However, under the same road condition driving condition, according to the present disclosure, two dual power transmission devices of 10KW each may be adopted, the total power is only 20KW, and the maximum torque is 9000N・M to 10,000 N·M (as shown in FIG. 5), and the two motors continue to operate in the high efficiency region of 95%. The large torque, which is more than 9000 N·M, can fully satisfy the driving of battery electric vehicles in all road conditions.

Comparing a conventional frequency conversion motor with a peak power of 60KW and a peak torque of 180N・M to the dual power transmission device of the present disclosure with a power of 20KW and a maximum torque of 9000N・M or more, it is equivalent. For a battery electric vehicle based on operating road conditions, if the transmission device of the present disclosure is adopted, the motor can continue to operate within the high efficiency operating speed range and avoid the low efficiency region of low speed operation due to frequency conversion. Therefore, the conclusion can be drawn that when driving under comparable road conditions, a motor with lower power may be selected and placed. Therefore, if the dual power planetary gear transmission device of the present disclosure is adopted for the conventional battery electric vehicle, it can greatly adapt to the driving conditions of the vehicle and greatly extend its mileage. Dual power sources in the present disclosure may select a controllable, adjustable speed high power internal combustion engine or other power machine when a high power and high torque output transmission device is required. The content of the present disclosure may be applied to other mechanical products that require forward/reverse rotational speed change.

The present disclosure provides a driving method for driving a transmission device as described above, wherein the transmission device includes a dual power source driving a planetary gear assembly, the planetary gear assembly including a sun gear 3 and a rotational gear. The dual power source includes an input shaft 14 connected to the sun gear 3 and a planetary gear 5 meshing between the sun gear 3 and the rotating internal tooth ring 4, the dual power source including an input shaft 14 connected to the sun gear 3, The dual power source is arranged to drive the sun gear 3 to rotate in a first direction relative to its own axis of rotation by a shaft 14, the dual power source being connected to the rotating internal gear ring 4 and The rotating internal toothed ring 4 is driven to rotate in a second direction opposite to the first direction with respect to its own axis of rotation, with the planetary gear 5 being driven to rotate with respect to its own axis of rotation. The planetary gear 5 rotates in the second direction, and the rotational direction of the planetary gear 5 around the input shaft 14 is determined by the linear velocity V1 of the pitch motion of the rotary internal gear ring 4 and the linear velocity V2 of the pitch motion of the sun gear 3. The present invention further provides a driving method.

According to one embodiment of the driving method described above, the dual power source includes a first power source 1 and a second power source 2, and the first power source 1 is connected to the sun gear by the input shaft 14. 3, and the second power source 2 is arranged to drive the rotary internal gear ring 4.

According to each embodiment of the driving method described above, the planetary gear 5 is attached to the planetary gear cage 6, the output shaft 7 is installed in the planetary gear cage 6, and the sun gear 3 is attached to the rotating inner gear ring 4. The output shaft 7 is coaxially installed with the input shaft 14.

According to each embodiment of the driving method described above, when the first direction is a clockwise direction, the second direction is a counterclockwise direction, and the first direction is a counterclockwise direction. In this case, the second direction is a clockwise direction.

According to each embodiment of the driving method described above, when V1>V2, the rotational direction of the planetary gear 5 and the planetary gear cage 6 around the input shaft 14 is opposite to the rotational direction of the input shaft 14. The direction of rotation of the output shaft 7 itself is opposite to the direction of rotation of the input shaft 14, and the tooth surface between the tooth surface of the planetary gear 5 and the tooth surface of the rotary internal gear ring 4 that meshes therewith. The gap is located only on one side of the teeth of the planetary gear 5. When the input shaft 14 drives the sun gear 3 to rotate in a counterclockwise direction relative to its own axis of rotation (not shown), the output shaft 7 itself rotates in a clockwise direction and the Those skilled in the art will understand that the tooth flank gap is located only on the left side of the teeth of the planetary gear 5, but the right side of the teeth of the planetary gear 5 is in contact with the tooth flank of the rotary internal gear ring 4.

When V1<V2, the rotation direction of the planetary gear 5 and the planetary gear cage 6 around the input shaft 14 is the same as the rotation direction of the input shaft 14, and the rotation direction of the output shaft 7 itself is the same as the rotation direction of the output shaft 7 itself. The direction of rotation is the same as the rotation direction of the input shaft 14, and the gap between the tooth surfaces of the planetary gear 5 and the tooth surface of the rotary internal tooth ring 4 that meshes therewith is on the one side of the teeth of the planetary gear 5. Retained. When the input shaft 14 drives the sun gear 3 to rotate in a counterclockwise direction relative to its own axis of rotation (not shown), the output shaft 7 itself rotates in a counterclockwise direction; It will be understood by those skilled in the art that the tooth flank gap is still located only on the left side of the teeth of the planetary gear 5, but the right side of the teeth of the planetary gear 5 is still in contact with the tooth flank of the rotating internal gear ring 4. It can be understood.

When V1=V2, the rotational speed of the planetary gear 5 and the planetary gear cage 6 around the input shaft 14 is zero, and the rotational speed of the output shaft 7 itself is zero.

According to each embodiment of the driving method described above, the first power source 1 is installed to have a constant power output, the second power source 2 is installed to have a speed adjustable power output, and the input control An electronic control device 11 is installed to handle errors in rotational speed drop or instability when the first power source 1 has different power depending on the line 13.

According to each embodiment of the driving method described above, when the second power source 2 rolls with the rotating internal tooth ring 4, the real-time data collection line 12 connected to the second power source 2 The motion data of the rotary internal tooth ring 4 is transmitted to the electronic control device 11, and the electronic control device 11 controls the power of the second power source 2 through the real-time data acquisition line 12 by processing an internal program or an external command. The output can be controlled and adjusted to allow said output shaft 7 to reach different speeds as required by the working situation.

According to each embodiment of the driving method described above, the first power source 1 is installed as a speed-adjustable power output, and the electronic control device 11 is connected to the first power source 1 by an input control line 13. Control power output.

According to each embodiment of the driving method described above, a parallel gear 8 is installed on the rotating internal gear ring 5, and an internal ring drive gear 9 driven by the second power source 2 meshes with the parallel gear 8. As a result, the rotary internal gear ring 4 is driven.

According to each embodiment of the driving method described above, the sun gear front gear 10 is installed on the input shaft 14, and the sun gear drive gear 15 driven by the first power source 1 is attached to the sun gear front gear 10. By meshing, the sun gear 3 is driven.

According to each embodiment of the driving method described above, the first power source and the second power source are installed like a controllable and speed adjustable power machine.

According to each embodiment of the drive method described above, the controllable, speed adjustable power machine is an electric motor or an internal combustion engine.

Below, the invention described in the original claims of the present application will be added.
[1] A transmission device having a dual power source, comprising a planetary gear assembly driven by the dual power source, the planetary gear assembly including a sun gear (3), a rotating internal gear ring (4), and a planetary gear assembly driven by the dual power source. a planetary gear (5) meshing between the sun gear (3) and the rotating internal gear ring (4);
Said dual power source includes an input shaft (14) connected to said sun gear (3), by said input shaft (14) said sun gear (3) in a first direction relative to its own axis of rotation. arranged to be driven to rotate;
The dual power source is connected to the rotating internal toothed ring (4) and rotates the rotating internal toothed ring (4) about its own axis of rotation in a second direction opposite to the first direction. the planetary gear (5) rotates in the second direction relative to its own axis of rotation;
The rotational direction of the planetary gear (5) around the input shaft (14) is determined by the linear velocity V1 of the pitch motion of the rotating internal gear ring (4) and the linear velocity V2 of the pitch motion of the sun gear (3). A transmission device with dual power sources.
[2] The dual power source includes a first power source (1) and a second power source (2),
the first power source (1) is arranged to drive the sun gear (3) by the input shaft (14);
The transmission device having dual power sources according to [1], wherein the second power source (2) is arranged to drive the rotating internal toothed ring (4).
[3] The planetary gear (5) is attached to a planetary gear cage (6) in which an output shaft (7) is installed,
the sun gear (3) is coaxially installed on the rotating internal gear ring (4);
The transmission device having a dual power source according to [1], wherein the output shaft (7) is installed coaxially with the input shaft (14).
[4] When the first direction is a clockwise direction, the second direction is a counterclockwise direction, and when the first direction is a counterclockwise direction, the second direction is a clockwise direction. The transmission device having a dual power source according to [3].
[5] When V1>V2, the direction of rotation of the planetary gear (5) and the planetary gear cage (6) around the input shaft (14) is opposite to the rotation direction of the input shaft (14). , the rotational direction of the output shaft (7) itself is opposite to the rotational direction of the input shaft (14), and the tooth surface of the planetary gear (5) and the tooth surface of the rotating internal gear ring (4) meshing therewith. The gap between the tooth surfaces is located only on one side of the teeth of the planetary gear (5),
When V1<V2, the rotational direction of the planetary gear (5) and the planetary gear cage (6) around the input shaft (14) is the same as the rotational direction of the input shaft (14), and the output The rotational direction of the shaft (7) itself is the same as the rotational direction of the input shaft (14), and the rotational direction between the tooth surface of the planetary gear (5) and the tooth surface of the rotary internal gear ring (4) meshing therewith is the same as the rotation direction of the input shaft (14). A tooth surface gap is maintained on the one side of the teeth of the planetary gear (5),
When V1=V2, the rotational speed of the planetary gear (5) and the planetary gear cage (6) around the input shaft (14) is zero, and the rotational speed of the output shaft (7) itself is zero. A transmission device having a dual power source according to [3] or [4].
[6] A parallel gear (8) is installed on the rotating internal gear ring (4),
The rotating internal ring (4) is driven by the internal ring gear (9) driven by the second power source (2) meshing with the parallel gear (8). Transmission device with dual power sources.
[7] A sun gear front gear (10) is installed on the input shaft (14),
The dual drive according to [5], wherein the sun gear (3) is driven by the input shaft gear (15) driven by the first power source (1) meshing with the sun gear front gear (10). A transmission device with a power source.
[8] The first power source (1) has a constant power output, and the second power source (2) has a speed adjustable power output,
The dual power source according to [5], wherein the electronic control device (11) uses the input control line (13) to process errors in rotational speed reduction or instability when the first power source (1) has different electric power. A transmission device having a
[9] When the second power source (2) rolls with the rotating internal tooth ring (4), the rotation is controlled by a real-time data acquisition line (12) connected to the second power source (2). motion data of the internal tooth ring (4) is transmitted to the electronic control device (11);
The electronic control unit (11) controls and adjusts the power output of the second power source (2) through the real-time data acquisition line (12) by processing an internal program or an external command, and controls the power output of the second power source (2) by processing the output shaft (7). ) can reach various speeds required in the working situation.
[10] The first power source (1) is a speed-adjustable power output, and the electronic control device (11) controls the power output of the first power source (1) by an input control line (13). , a transmission device having dual power sources according to [5].
[11] The transmission device having dual power sources according to [1], wherein the first power source and the second power source are controllable and speed adjustable power machines.
[12] The transmission device with dual power sources according to [10], wherein the controllable and speed adjustable power machine is an electric motor or an internal combustion engine.
[13] An electric vehicle comprising the transmission device having a dual power source according to any one of [1] to [12].
[14] A driving method for driving the transmission device according to any one of [1] to [12], wherein the transmission device includes a dual power source that drives a planetary gear assembly, and the planetary gear assembly includes: comprising a sun gear (3), a rotating internal toothed ring (4), and a planetary gear (5) meshing between the sun gear (3) and the rotating internal toothed ring (4);
Said dual power source includes an input shaft (14) connected to said sun gear (3), by said input shaft (14) said sun gear (3) in a first direction relative to its own axis of rotation. arranged to be driven to rotate;
The dual power source is connected to the rotating internal toothed ring (4) and rotates the rotating internal toothed ring (4) about its own axis of rotation in a second direction opposite to the first direction. the planetary gear (5) rotates in the second direction relative to its own axis of rotation;
The rotational direction of the planetary gear (5) around the input shaft (14) is determined by the linear velocity V1 of the pitch motion of the rotating internal gear ring (4) and the linear velocity V2 of the pitch motion of the sun gear (3). driving method.
[15] The dual power source includes a first power source (1) and a second power source (2),
the first power source (1) is arranged to drive the sun gear (3) by the input shaft (14);
The driving method according to [14], wherein the second power source (2) is arranged to drive the rotating internal toothed ring (4).
[16] The planetary gear (5) is attached to the planetary gear cage (6), the output shaft (7) is installed in the planetary gear cage (6),
the sun gear (3) is coaxially installed on the rotating internal gear ring (4);
The driving method according to [14], wherein the output shaft (7) is installed coaxially with the input shaft (14).
[17] When the first direction is a clockwise direction, the second direction is a counterclockwise direction, and when the first direction is a counterclockwise direction, the second direction is a clockwise direction. The driving method according to [16].
[18] When V1>V2, the direction of rotation of the planetary gear (5) and the planetary gear cage (6) around the input shaft (14) is opposite to the rotation direction of the input shaft (14). , the rotational direction of the output shaft (7) itself is opposite to the rotational direction of the input shaft (14), and the tooth surface of the planetary gear (5) and the tooth surface of the rotating internal gear ring (4) meshing therewith. The gap between the tooth surfaces is located only on one side of the teeth of the planetary gear (5),
When V1<V2, the rotational direction of the planetary gear (5) and the planetary gear cage (6) around the input shaft (14) is the same as the rotational direction of the input shaft (14), and the output The rotational direction of the shaft (7) itself is the same as the rotational direction of the input shaft (14), and the rotational direction between the tooth surface of the planetary gear (5) and the tooth surface of the rotary internal gear ring (4) meshing therewith is the same as the rotation direction of the input shaft (14). A tooth surface gap is maintained on the one side of the teeth of the planetary gear (5),
When V1=V2, the rotational speed of the planetary gear (5) and the planetary gear cage (6) around the input shaft (14) is zero, and the rotational speed of the output shaft (7) itself is zero. The driving method according to [17].
[19] The first power source (1) is installed as a constant power output, and the second power source (2) is installed as a speed adjustable power output,
The driving method according to [18], further comprising installing an electronic control device (11) that processes errors in rotational speed drop or instability when the first power source (1) has different electric power depending on the input control line (13). .
[20] The second power source (2) rolls with the rotating inner toothed ring (4), and the real-time data acquisition line (12) connected to the second power source (2) motion data of the tooth ring (4) are transmitted to said electronic control device (11);
The electronic control unit (11) controls and adjusts the power output of the second power source (2) through the real-time data acquisition line (12) by processing an internal program or an external command, and controls the power output of the second power source (2) by processing the output shaft (7). ) can reach various speeds required in the working situation.
[21] The first power source (1) is installed as a speed adjustable power output, and the electronic control device (11) controls the power output of the first power source (1) by an input control line (13). The driving method according to [18], which controls.
[22] The driving method according to [14], wherein the first power source and the second power source are installed like controllable and speed-adjustable power machines.
[23] The drive method according to [22], wherein the controllable, speed-adjustable power machine is an electric motor or an internal combustion engine.
[24] A parallel gear (8) is installed on the rotating internal toothed ring (5), and an internal ring gear (9) driven by the second power source (2) meshes with the parallel gear (8). Accordingly, the driving method according to [18], wherein the rotating internal tooth ring (4) is driven.
[25] A sun gear front gear (10) is installed on the input shaft (14), and the input shaft gear (15) driven by the first power source (1) meshes with the sun gear front gear (10). The driving method according to [18], wherein the sun gear (3) is driven.

Claims (10)

A transmission device with dual power sources, comprising a planetary gear assembly driven by said dual power sources, said planetary gear assembly including a sun gear (3), a rotating internal gear ring (4), and said sun gear ( 3) and a planetary gear (5) meshing with the rotating internal toothed ring (4),
The dual power source includes an input shaft (14) connected to the sun gear (3), the input shaft (14) driving the sun gear (3) in a first direction relative to its own axis of rotation. arranged to be driven to rotate;
The dual power source is connected to the rotating internal toothed ring (4) and rotates the rotating internal toothed ring (4) about its own axis of rotation in a second direction opposite to the first direction. the planetary gear (5) rotates in the second direction relative to its own axis of rotation;
The rotational direction of the planetary gear (5) around the input shaft (14) is determined by the linear velocity V1 of the pitch motion of the rotating internal gear ring (4) and the linear velocity V2 of the pitch motion of the sun gear (3). is,
The dual power source includes a first power source (1) and a second power source (2),
the first power source (1) is arranged to drive the sun gear (3) by the input shaft (14);
the second power source (2) is arranged to drive the rotating internal toothed ring (4);
the first power source (1) and the second power source (2) are installed on the same side of the planetary gear assembly ;
A parallel gear (8) is installed on the rotating internal toothed ring (4), and the tooth surface (16) of the rotating internal toothed ring (4) and the parallel gear (8) are aligned with an axis along the input shaft (14). away in the direction,
The internal toothed ring drive gear (9) driven by the second power source (2) meshes with the parallel gear (8), thereby driving the rotating internal toothed ring (4),
A sun gear front gear (10) is installed on the input shaft (14),
The sun gear drive gear (15) driven by the first power source (1) meshes with the sun gear front gear (10), thereby driving the sun gear (3). connected to the sun gear front gear (10) only via the input shaft (14);
The sun gear (3) and the sun gear front gear (10) are each arranged on both sides of the parallel gear (8) along the axial direction of the input shaft (14),
In the axial direction along the input shaft (14), the sun gear front gear (10) is located between the rotating internal gear ring (4) and the first power source (1), and the rotating internal gear located between the ring (4) and the second power source (2);
Transmission device with dual power sources. The planetary gear (5) is attached to a planetary gear cage (6) in which an output shaft (7) is installed,
the sun gear (3) is coaxially installed on the rotating internal gear ring (4);
The transmission device with dual power sources according to claim 1, wherein the output shaft (7) is coaxially installed with the input shaft (14). when the first direction is a clockwise direction, the second direction is a counterclockwise direction,
The transmission device with dual power sources according to claim 2, wherein when the first direction is a counterclockwise direction, the second direction is a clockwise direction. When V1>V2, the rotational direction of the planetary gear (5) and the planetary gear cage (6) around the input shaft (14) is opposite to the rotational direction of the input shaft (14), and the output The direction of rotation of the shaft (7) itself is opposite to the direction of rotation of the input shaft (14), and the rotation direction between the tooth surface of the planetary gear (5) and the tooth surface of the rotary internal gear ring (4) that meshes with it is The gap between the tooth surfaces is located only on one side of the teeth of the planetary gear (5),
When V1<V2, the rotational direction of the planetary gear (5) and the planetary gear cage (6) around the input shaft (14) is the same as the rotational direction of the input shaft (14), and the output The rotational direction of the shaft (7) itself is the same as the rotational direction of the input shaft (14), and the rotational direction between the tooth surface of the planetary gear (5) and the tooth surface of the rotary internal gear ring (4) meshing therewith is the same as the rotation direction of the input shaft (14). A tooth surface gap is maintained on the one side of the teeth of the planetary gear (5),
When V1=V2, the rotational speed of the planetary gear (5) and the planetary gear cage (6) around the input shaft (14) is zero, and the rotational speed of the output shaft (7) itself is zero. A transmission device having a dual power source according to claim 2 or 3. the first power source (1) is a constant power output; the second power source (2) is a speed adjustable power output;
Dual power source according to claim 4, wherein the electronic control device (11) handles the error of rotational speed drop or instability when the first power source (1) is at different power by means of an input control line (13). A transmission device having a When the second power source (2) rolls with the rotating internal tooth ring (4), the rotating internal tooth ring (4) is controlled by a real-time data acquisition line (12) connected to the second power source (2). (4) the motion data is transmitted to the electronic control device (11);
The electronic control unit (11) controls and adjusts the power output of the second power source (2) through the real-time data acquisition line (12) by processing an internal program or an external command, and controls the power output of the second power source (2) by processing the output shaft (7). 6. The transmission device with dual power sources according to claim 5 , wherein the transmission device is capable of reaching various speeds required in the working situation. Claim: wherein the first power source (1) is a speed-adjustable power output, and wherein the electronic control device (11) controls the power output of the first power source (1) by an input control line (13). 5. The transmission device having dual power sources according to 5 . The transmission apparatus with dual power sources of claim 1, wherein the first power source and the second power source are controllable, adjustable speed power machines. 8. A transmission device with dual power sources as claimed in claim 7 , wherein the controllable speed adjustable power machine is an electric motor or an internal combustion engine. An electric vehicle comprising a transmission device having dual power sources according to any one of claims 1 to 9 .